Abstract:

A torque distribution control apparatus for a four-wheel drive vehicle
includes a vehicle-speed detector configured to detect a vehicle speed of
the vehicle. A wheel-speed detector is configured to detect wheel speeds
of main driving wheels and sub-driving wheels of the vehicle. A
sub-driving-wheel distribution-torque calculator is configured to
calculate a sub-driving-wheel distribution torque in accordance with a
rotation speed difference between the main driving wheels and the
sub-driving wheels calculated based on an output from the wheel-speed
detector. A torque limiter is configured to limit an upper limit of the
sub-driving-wheel distribution torque. A controller is configured to
control the sub-driving-wheel distribution torque to be transmitted to
the right and left sub-driving wheels by right and left torque
distribution clutches in accordance with a driving state of the vehicle.

Claims:

1. A torque distribution control apparatus for a four-wheel drive vehicle,
comprising:a vehicle-speed detector configured to detect a vehicle speed
of the four-wheel drive vehicle which includes:right and left main
driving wheels to which a driving torque output from a driving source is
directly transmitted; andright and left sub-driving wheels to which the
driving torque is transmitted via right and left torque distribution
clutches;a wheel-speed detector configured to detect wheel speeds of the
main driving wheels and the sub-driving wheels;a sub-driving-wheel
distribution-torque calculator configured to calculate a
sub-driving-wheel distribution torque in accordance with a rotation speed
difference between the main driving wheels and the sub-driving wheels
calculated based on an output from the wheel-speed detector;a torque
limiter configured to limit an upper limit of the sub-driving-wheel
distribution torque when the sub-driving-wheel distribution torque
calculated by the sub-driving-wheel distribution-torque calculator is
higher than or equal to a first predetermined value, both a rotation
speed difference of the left torque distribution clutch and a rotation
speed difference of the right torque distribution clutch are larger than
or equal to a second predetermined value, and the vehicle speed detected
by the vehicle-speed detector is lower than or equal to a third
predetermined value; anda controller configured to control the
sub-driving-wheel distribution torque to be transmitted to the right and
left sub-driving wheels by the right and left torque distribution
clutches in accordance with a driving state of the vehicle.

2. The torque distribution control apparatus according to claim 1, further
comprising:a road-gradient detector configured to detect a gradient of a
road surface,wherein the torque limiter limits the upper limit of the
sub-driving-wheel distribution torque when the gradient of the road
surface detected by the road-gradient detector is smaller than or equal
to a fourth predetermined value.

3. A torque distribution control apparatus for a four-wheel drive vehicle,
comprising:vehicle-speed detection means for detecting a vehicle speed of
the four-wheel drive vehicle which includes:right and left main driving
wheels to which a driving torque output from a driving source is directly
transmitted; andright and left sub-driving wheels to which the driving
torque is transmitted via right and left torque distribution
clutches;wheel-speed detection means for detecting wheel speeds of the
main driving wheels and the sub-driving wheels;sub-driving-wheel
distribution-torque calculation means for calculating a sub-driving-wheel
distribution torque in accordance with a rotation speed difference
between the main driving wheels and the sub-driving wheels calculated
based on an output from the wheel-speed detection means;torque limiting
means for limiting an upper limit of the sub-driving-wheel distribution
torque when the sub-driving-wheel distribution torque calculated by the
sub-driving-wheel distribution-torque calculation means is higher than or
equal to a first predetermined value, both a rotation speed difference of
the left torque distribution clutch and a rotation speed difference of
the right torque distribution clutch are larger than or equal to a second
predetermined value, and the vehicle speed detected by the vehicle-speed
detection means is lower than or equal to a third predetermined value;
andcontrolling means for controlling the sub-driving-wheel distribution
torque to be transmitted to the right and left sub-driving wheels by the
right and left torque distribution clutches in accordance with a driving
state of the vehicle.

4. The torque distribution control apparatus according to claim 3, further
comprising:road-gradient detecting means for detecting a gradient of a
road surface,wherein the torque limiting means limits the upper limit of
the sub-driving-wheel distribution torque when the gradient of the road
surface detected by the road-gradient detecting means is smaller than or
equal to a fourth predetermined value.

5. A four-wheel drive vehicle comprising:right and left main driving
wheels to which a driving torque output from a driving source is directly
transmitted;right and left sub-driving wheels to which the driving torque
is transmitted via right and left torque distribution clutches; anda
torque distribution control apparatus comprising:a vehicle-speed detector
configured to detect a vehicle speed of the four-wheel drive vehicle;a
wheel-speed detector configured to detect wheel speeds of the main
driving wheels and the sub-driving wheels;a sub-driving-wheel
distribution-torque calculator configured to calculate a
sub-driving-wheel distribution torque in accordance with a rotation speed
difference between the main driving wheels and the sub-driving wheels
calculated based on an output from the wheel-speed detector;a torque
limiter configured to limit an upper limit of the sub-driving-wheel
distribution torque when the sub-driving-wheel distribution torque
calculated by the sub-driving-wheel distribution-torque calculator is
higher than or equal to a first predetermined value, both a rotation
speed difference of the left torque distribution clutch and a rotation
speed difference of the right torque distribution clutch are larger than
or equal to a second predetermined value, and the vehicle speed detected
by the vehicle-speed detector is lower than or equal to a third
predetermined value; anda controller configured to control the
sub-driving-wheel distribution torque to be transmitted to the right and
left sub-driving wheels by the right and left torque distribution
clutches in accordance with a driving state of the vehicle.

Description:

CROSS REFERENCES TO RELATED APPLICATIONS

[0001]The present application claims priority under 35 U.S.C.§119 to
Japanese Patent Application No. 2009-182213, filed Aug. 5, 2009, entitled
"Torque Distribution Control Device for Four-Wheel Drive Vehicle." The
contents of this application are incorporated by reference in their
entirety.

BACKGROUND OF THE INVENTION

[0002]1. Field of the Invention

[0003]The present invention relates to a torque distribution control
apparatus for a four-wheel drive vehicle and a four-wheel drive vehicle
having the torque distribution control apparatus.

[0004]2. Description of the Related Art

[0005]Japanese Patent No. 3603569 discloses that driving force output from
an engine is transmitted to a transmission via a clutch and driving force
output from the transmission is transmitted to driving wheels via a power
transmission system such as a differential gear. When a quick
acceleration request is made by the driver, the engine speed or the
engine output torque is limited so as to prevent the differential gear
from damage.

[0006]When front wheels serving as main driving wheels slip and a rotation
speed difference is produced between the front wheels and rear wheels
serving as sub-driving wheels at the start of a four-wheel drive vehicle,
driving-force distribution clutches in the rear differential gear are
engaged to distribute the driving torque to the rear wheels. Thereby, the
driving torque to be distributed to the front wheels is reduced to
suppress the slip, and traction is produced in the rear wheels so that
the vehicle can start moving. If an actual driving torque produced in the
rear wheels by engagement of the torque distribution clutches excessively
increases, the load on the rear differential gear increases, and this may
reduce durability.

[0007]By limiting the engine speed or the engine output torque, as in the
invention of Japanese Patent No. 3603569, the driving torque to be
distributed to the rear wheels can be reduced and the rear differential
gear can be protected. In this case, unfortunately, the total traction of
the front wheels and the rear wheels decreases, and this reduces starting
performance of the vehicle.

SUMMARY OF THE INVENTION

[0008]According to an aspect of the present invention, a torque
distribution control apparatus for a four-wheel drive vehicle includes a
vehicle-speed detector, a wheel-speed detector, a sub-driving-wheel
distribution-torque calculator, a torque limiter, and a controller. The
vehicle-speed detector is configured to detect a vehicle speed of the
four-wheel drive vehicle. The four-wheel drive vehicle includes right and
left main driving wheels to which a driving torque output from a driving
source is directly transmitted, and right and left sub-driving wheels to
which the driving torque is transmitted via right and left torque
distribution clutches. The wheel-speed detector is configured to detect
wheel speeds of the main driving wheels and the sub-driving wheels. The
sub-driving-wheel distribution-torque calculator is configured to
calculate a sub-driving-wheel distribution torque in accordance with a
rotation speed difference between the main driving wheels and the
sub-driving wheels calculated based on an output from the wheel-speed
detector. The torque limiter is configured to limit an upper limit of the
sub-driving-wheel distribution torque when the sub-driving-wheel
distribution torque calculated by the sub-driving-wheel
distribution-torque calculator is higher than or equal to a first
predetermined value, both a rotation speed difference of the left torque
distribution clutch and a rotation speed difference of the right torque
distribution clutch are larger than or equal to a second predetermined
value, and the vehicle speed detected by the vehicle-speed detector is
lower than or equal to a third predetermined value. The controller is
configured to control the sub-driving-wheel distribution torque to be
transmitted to the right and left sub-driving wheels by the right and
left torque distribution clutches in accordance with a driving state of
the vehicle.

[0009]According to another aspect of the present invention, a four-wheel
drive vehicle includes right and left main driving wheels, right and left
sub-driving wheels, and a torque distribution control apparatus. To the
right and left main driving wheels, a driving torque output from a
driving source is directly transmitted. To the right and left sub-driving
wheels, the driving torque is transmitted via right and left torque
distribution clutches. The torque distribution control apparatus includes
a vehicle-speed detector, a wheel-speed detector, a sub-driving-wheel
distribution-torque calculator, a torque limiter, and a controller. The
vehicle-speed detector is configured to detect a vehicle speed of the
four-wheel drive vehicle. The wheel-speed detector is configured to
detect wheel speeds of the main driving wheels and the sub-driving
wheels. The sub-driving-wheel distribution-torque calculator is
configured to calculate a sub-driving-wheel distribution torque in
accordance with a rotation speed difference between the main driving
wheels and the sub-driving wheels calculated based on an output from the
wheel-speed detector. The torque limiter is configured to limit an upper
limit of the sub-driving-wheel distribution torque when the
sub-driving-wheel distribution torque calculated by the sub-driving-wheel
distribution-torque calculator is higher than or equal to a first
predetermined value, both a rotation speed difference of the left torque
distribution clutch and a rotation speed difference of the right torque
distribution clutch are larger than or equal to a second predetermined
value, and the vehicle speed detected by the vehicle-speed detector is
lower than or equal to a third predetermined value. The controller is
configured to control the sub-driving-wheel distribution torque to be
transmitted to the right and left sub-driving wheels by the right and
left torque distribution clutches in accordance with a driving state of
the vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

[0010]A more complete appreciation of the invention and many of the
attendant advantages thereof will be readily obtained as the same becomes
better understood by reference to the following detailed description when
considered in connection with the accompanying drawings, wherein:

[0011]FIG. 1 illustrates a driving-force transmission system of a
four-wheel drive vehicle;

[0012]FIG. 2 is an enlarged view of a speed-increasing device and a rear
differential gear;

[0013]FIG. 3 is a block diagram of a four-wheel drive electronic control
unit;

[0015]FIG. 5 is a flowchart showing the clutch-torque limiting control.

DESCRIPTION OF THE EMBODIMENTS

[0016]An embodiment of the present invention will be described below with
reference to FIGS. 1 to 5.

[0017]Referring to FIG. 1, a four-wheel drive vehicle to which the
embodiment of the present invention is applied includes right and left
front wheels Wf serving as main driving wheels, and right and left rear
wheels Wr serving as sub-driving wheels. Basically, during driving of the
vehicle, the right and left front wheels Wf are constantly driven, and
the right and left rear wheels Wr are appropriately driven in accordance
with a driving state of the vehicle.

[0018]An automatic transmission T is connected to an engine E that is
transversely mounted at the front of a vehicle body, and is also
connected to the right and left front wheels Wf via a front differential
gear 11 and right and left front drive shafts 12. The front differential
gear 11 is connected to the right and left rear wheels Wr via a transfer
(not shown), a front propeller shaft 13, a speed-increasing device 14, a
rear propeller shaft 15, a rear differential gear 16, and right and left
rear drive shafts 17.

[0020]The planetary gear mechanism 21 includes an input-side sun gear 24
fixed to a rear end of the front propeller shaft 13, an output-side sun
gear 25 fixed to a front end of the rear propeller shaft 15, a carrier
26, and a plurality of double pinions 27 supported by the carrier 26.
Each double pinion 27 has an input-side pinion 27a and an output-side
pinion 27b provided integrally. The number of teeth of the output-side
pinion 27b is set to be larger than the number of teeth of the input-side
pinion 27a. Correspondingly, the number of teeth of the output-side sun
gear 25 is set to be smaller than the number of teeth of the input-side
sun gear 24.

[0021]The speed-increasing clutch 22 is of a hydraulic multi-plate type.
In the speed-increasing clutch 22, a clutch outer 29 fixed to a housing
28 and a clutch inner 30 provided on an inner side of the clutch outer 29
oppose with a plurality of frictional engaging elements 31 being disposed
therebetween. When the frictional engaging elements 31 are engaged by the
supply of hydraulic pressure, the clutch inner 30 is engaged with the
clutch outer 29 and is thereby restrained by the housing 28 so as not to
rotate.

[0022]The directly-coupled clutch 23 is of a hydraulic multi-plate type,
and includes a clutch outer 32 provided integrally with the clutch inner
30 of the speed-increasing clutch 22 and the carrier 26 of the planetary
gear mechanism 21, a clutch inner 33 provided integrally with the front
propeller shaft 13, a plurality of frictional engaging elements 34
provided between the clutch outer 32 and the clutch inner 33, and a
one-way clutch 35 provided between the clutch outer 32 and the clutch
inner 33. When the rotation speed of the clutch inner 33 exceeds the
rotation speed of the clutch outer 32, the one-way clutch 35 slips to
block transmission of the driving force. When the frictional engaging
elements 34 are engaged by the supply of hydraulic pressure, the clutch
outer 32 is engaged with the clutch inner 33, so that the front propeller
shaft 13 is combined with the carrier 26 of the planetary gear mechanism
21.

[0023]Accordingly, when the speed-increasing clutch 22 is engaged and the
directly-coupled clutch 23 is disengaged, the carrier 26 of the planetary
gear mechanism 21 is restrained by the housing 28 so as to not to rotate.
Hence, the rotation speed of the front propeller shaft 13 is increased by
the speed increasing ratio (e.g., 1.05) determined by the numbers of
teeth of the input-side sun gear 24, the output-side sun gear 25, and the
double pinions 27, and the increased rotation speed is output to the rear
propeller shaft 15.

[0024]Conversely, when the speed-increasing clutch 22 is disengaged and
the directly-coupled clutch 23 is engaged, the input-side sun gear 24 and
the carrier 26 of the planetary gear mechanism 21 are combined into a
lock state, so that the rotation of the front propeller shaft 13 is
output to the rear propeller shaft 15 without any change.

[0025]Since the rear differential gear 16 has a structure that is
substantially symmetrical with respect to the vehicle center plane in the
front-right direction, only a structure of a part on the left side of the
vehicle center plane will be described below.

[0026]A driven bevel gear 37 is fixed to a center portion of an input
shaft 36 coaxially provided between opposing ends of the left and rear
drive shafts 17, and engages with a driving bevel gear 38 fixed to a rear
end of the rear propeller shaft 15. Between the input shaft 36 and the
left rear drive shaft 17, a planetary gear mechanism 39 and an
electromagnetic multi-plate torque distribution clutch 40 are provided.

[0027]The planetary gear mechanism 39 includes a ring gear 41, a carrier
42, a sun gear 43, and a plurality of pinions 44 that are supported by
the carrier 42 and simultaneously engage with the ring gear 41 and the
sun gear 43. The ring gear 41 is coupled to a left end of the input shaft
36, and the carrier 42 is coupled to a right end of the left rear drive
shaft 17.

[0028]The torque distribution clutch 40 includes a clutch outer 46 fixed
to a housing 45, a clutch inner 47 coupled to the sun gear 43 in the
planetary gear mechanism 39, a plurality of frictional engaging elements
48 provided between the clutch outer 46 and the clutch inner 47, and an
electromagnetic actuator 49 (see FIG. 1) that engages the frictional
engaging elements 48 so as to combine the clutch outer 46 and the clutch
inner 47.

[0029]In a state in which the electromagnetic actuator 49 is off, the
torque distribution clutch 40 is disengaged, and therefore, the sun gear
43 is freely movable. Hence, the driving force of the input shaft 36 is
not transmitted to the left rear drive shaft 17. In contrast, in a state
in which the electromagnetic actuator 49 is on and the torque
distribution clutch 40 is engaged, the sun gear 43 is restrained by the
housing 45 so as to not to rotate. Hence, the driving force of the input
shaft 36 is transmitted to the left rear drive shaft 17.

[0030]In this case, when the slip amount of the torque distribution clutch
40 is changed by changing the current to be supplied to the
electromagnetic actuator 49, the torque to be transmitted from the input
shaft 36 to the left rear drive shaft 17 can be changed continuously.

[0031]Accordingly, by changing the engaging forces of the right and left
torque distribution clutches 40 of the rear differential gear 16, the
ratio of torques distributed between the front wheels Wf and the rear
wheels Wr can be arbitrarily controlled, and the ratio of torques
distributed between the right and left rear wheels Wr can be controlled
arbitrarily.

[0032]Next, a description will be given of a four-wheel drive (4WD)
electronic control unit Ua for controlling operations of the
speed-increasing device 14 and the rear differential gear 16, with
reference to FIG. 3.

[0033]An FI/AT electronic control unit Ub for controlling the operations
of the engine E and the automatic transmission T and an electronic
stability control (ESC) electronic control unit Uc for controlling the
operation of a vehicle-behavior stabilization system are connected via a
controller area network (CAN) to an input unit 51 of the 4WD electronic
control unit Ua. Further, a vehicle-speed sensor 52a for detecting the
vehicle speed, for example, from the rotation speed of a gear in the
automatic transmission T, and a steering-angle sensor 52b for detecting
the steering angle of a steering wheel are connected to the input unit
51.

[0034]Signals input from the FI/AT electronic control unit Ub to the input
unit 51 include the engine speed, suction negative pressure, rotation
speeds of a main shaft and a countershaft of the automatic transmission
T, and shift position of the automatic transmission T. Further, signals
input from the ESC electronic control unit Uc to the input unit 51
include the wheel speeds of the front wheels Wr and the rear wheels Wr,
lateral acceleration of the vehicle, and longitudinal acceleration of the
vehicle.

[0035]An estimated-driving-torque calculation unit 53 calculates an
estimated driving torque output from the transmission T on the basis of
the engine speed, the suction negative pressure (or suction flow rate),
the gear ratio estimated from the rotation speeds of the main shaft and
the countershaft, the speed ratio of a torque converter, and efficiencies
of the gear stages, which are input from the input unit 51. Instead of
estimating the gear ratio from the rotation speeds of the main shaft and
the countershaft, the gear ratio of the shift position detected by a
shift position sensor may be used.

[0036]A driving-stability control unit 54 calculates a driving-stability
control torque to be distributed to the right and left rear wheels Wr on
the basis of the estimated driving torque calculated by the
estimated-driving-torque calculation unit 53 and the lateral
acceleration, steering angle, and wheel speeds input from the input unit
51. For example, when the slip angle of the vehicle is larger than or
equal to a predetermined value, the driving-stability control unit 54
determines that vehicle behavior is unstable, and controls the rear
differential gear 16 so as to reduce the torque to be distributed to the
right and left rear wheels Wr and to reduce the torque to be distributed
to a turning outside wheel of the right and left rear wheels Wr, thereby
stabilizing the vehicle behavior.

[0037]When the vehicle speed is medium and the lateral acceleration is
high, a speed-increase control unit 55 engages the speed-increasing
clutch 22 of the speed-increasing device 14 so as to increase the
rotation speed of the rear propeller shaft 15 with respect to the
rotation speed of the front propeller shaft 13, and distributes the
torque to a turning outside wheel of the right and left rear wheels Wr by
the rear differential gear 16, thereby improving turning performance
while avoiding understeering of the vehicle. When the vehicle speed is
low or high and the lateral acceleration is low, the speed-increase
control unit 55 engages the directly-coupled clutch 23 of the
speed-increasing device 14, and stops the operation of increasing the
rotation speed of the rear propeller shaft 15 with respect to the
rotation speed of the front propeller shaft 13. In this state, the
speed-increase control unit 55 distributes the torque to the turning
outer wheel of the right and left rear wheels Wr by the rear differential
gear 16 so as to ensure a stable turning performance.

[0038]When the driving-stability control unit 54 outputs a request to
inhibit the speed increase because the speed increase may disturb the
vehicle behavior, operation of the speed-increasing device 14 is
inhibited.

[0039]A limited slip differential (LSD) control unit 56 compares the wheel
speeds of the right and left front wheels Wf with the wheel speeds of the
right and left rear wheels Wr. When the front wheels Wr slip because the
frictional coefficient of a road surface on which the front wheels Wr
move at the start of the vehicle is lower than the frictional coefficient
of a road surface on which the rear wheels Wr move, the LSD control unit
56 calculates an LSD torque to be distributed to the rear wheels Wr in
accordance with a rotation speed difference between the front wheels and
the rear wheels. When the LSD torque is distributed to the rear wheels Wr
by the rear differential gear 16, the slip of the front wheels Wf is
reduced, and the vehicle is allowed to smoothly start moving.

[0040]A climbing control unit 58 compares an actual longitudinal
acceleration detected by a longitudinal-acceleration sensor with an
estimated longitudinal acceleration obtained by differentiating the
vehicle speed so as to calculate a climbing angle (gradient of an uphill
road) of the vehicle. Then, the climbing control unit 58 calculates a
climbing start torque to be distributed to the rear wheels Wr by the rear
differential gear 16 in accordance with the climbing angle in order to
increase the climbing force used when the vehicle starts moving on the
uphill road.

[0041]A torque addition unit 57 adds the driving-stability control torque
calculated by the driving-stability control unit 54, the LSD torque
calculated by the LSD control unit 56, and the climbing start torque
calculated by the climbing control unit 58.

[0042]A clutch-torque limiter 60 outputs a clutch torque command obtained
by limiting a target torque to be transmitted to the rear wheels Wr by
the rear differential gear 16 by an upper limit in order to prevent
durability from being reduced by an excessive load acting on the rear
differential gear 16 at the start of the vehicle on the uphill road. This
control will be described in detail below with reference to FIG. 4.

[0043]A current control unit 61 converts the clutch torque command
calculated by the clutch-torque limiter 60 into a current value (PWM
value) to be supplied to the electromagnetic actuators 49 of the torque
distribution clutches 40 in the rear differential gear 16.

[0044]Then, a driving circuit unit 62 controls the operation of the
speed-increasing device 14 on the basis of a speed increase command
output from the speed-increase control unit 55, and controls the
operation of the rear differential gear 16 on the basis of the current
value output from the current control unit 61.

[0045]Next, with reference to FIG. 4, a description will be given of logic
of torque control over the rear differential gear 16 exerted in the
climbing control unit 58 and the clutch-torque limiter 60 when the
vehicle start moving on an uphill road.

[0046]When the vehicle starts moving on an uphill road, the weight of the
vehicle is moved from the side of the front wheels Wf to the side of the
rear wheels Wr by the inclination of the road surface, and a component of
gravity in a direction of the road surface tries to reverse the vehicle.
Hence, the front wheels Wf serving as the main driving wheels easily
slip. This tendency is pronounced particularly when the coefficient of
friction of a road surface on which the front wheels Wf move is lower
than the coefficient of friction of a road surface on which the rear
wheels Wr move (a so-called longitudinally split μ-road).

[0047]When the front wheels Wf slip and a rotation speed difference is
caused between the front wheels Wf and the rear wheels Wr in this state,
the right and torque distribution clutches 40 in the rear differential
gear 16 are engaged by longitudinal LSD control, thereby distributing the
driving torque to the rear wheels Wr. This reduces the slip of the front
wheels Wf and produces traction in the rear wheels Wr so that the vehicle
can start moving.

[0048]However, if the target distribution torque to be distributed to the
rear wheels Wr increases in a state in which a rapid differential
rotation is produced in the right and left torque distribution clutches
40 of the rear differential gear 16, an actual driving torque to be
actually transmitted to the rear wheels Wr by engagement of the right and
left torque distribution clutches 40 excessively increases. Consequently,
the load on the rear differential gear 16 may increase and this may
reduce durability. For this reason, control for protecting the rear
differential gear 16 is exerted by limiting the upper limit of the target
distribution torque to be distributed to the right and left rear wheels
Wr when predetermined conditions are satisfied.

[0049]As shown in FIG. 4, the predetermined conditions are the following
four conditions: [0050](1) The total target distribution torque to be
transmitted to the right and left rear wheels Wr is higher than or equal
to a predetermined value (300 kgfm in the embodiment). [0051](2) Rotation
speed differences between the clutch outers 46 and the clutch inners 47
in the right and left torque distribution clutches 40 are both more than
or equal to a predetermined value (300 rpm in the embodiment). [0052](3)
The vehicle speed is lower than or equal to a predetermined value (5 km/h
in the embodiment). [0053](4) The climbing angle converted into a gravity
acceleration G is less than or equal to a predetermined value (0.2 G in
the embodiment).

[0054]When all of the four conditions are satisfied, control is exerted so
as to make the upper limit of the driving torque to be distributed to the
rear wheels Wr lower than in a normal condition.

[0055]The above condition (2) is set for the following reason. The driving
torque is limited when the coefficient of friction of the road surface on
which the front wheels Wf move is different from the coefficient of
friction of the road surface on which the rear wheels Wr move (a
so-called longitudinally split μ-road) and the rotation speed
differences between the clutch outers 46 and the clutch inners 47 of the
right and left torque distribution clutches 40 in the rear differential
gear 16 are both more than or equal to the predetermined value. This
prevents the rear differential gear 16 from being overloaded by an
excessive actual driving torque.

[0056]The above condition (3) is set because this control is originally
directed to the start of the vehicle when the vehicle speed is low.

[0057]The above condition (4) is set for the following reason. If the
driving torque to be distributed to the rear wheels Wr is limited in a
state in which the climbing angle exceeds the predetermined value, the
vehicle cannot climb on a sharp uphill road, and climbing performance may
be reduced.

[0058]The above condition (4) is not essential. The driving torque to be
distributed to the rear wheels Wr may be limited when only the conditions
(1), (2), and (3) are satisfied.

[0059]FIG. 5 is a flowchart showing the above-described operations. When
the target distribution torque of the right and left rear wheels Wr is
higher than or equal to 300 kgfm in Step S1, the rotation speed
differences of the right and left torque distribution clutches 40 are
both more than or equal to 300 rpm in Step S2, the vehicle speed is lower
than or equal to 5 km/h in Step S3, and the climbing angle of the road
surface is less than or equal to 0.2 in Step S4, the upper limit of the
target distribution torque is limited in Step S5. When any of the
conditions of Steps S1 to S4 is not satisfied, the upper limit of the
target distribution torque is not limited in Step S6. Therefore,
durability of the rear differential gear 16 is prevented from being
reduced by distribution of an excessive actual driving torque to the rear
wheels Wr without reducing driving ability on the longitudinally split
μ-road and climbing ability on the uphill road. Moreover, since there
is no need to reduce the output torque from the engine E, reduction of
starting performance of the vehicle can be minimized.

[0060]While the embodiment of the present invention has been described
above, various design variations are possible without departing from the
scope of the invention.

[0061]For example, the driving source of the embodiment of the present
invention is not limited to the engine E of the embodiment, and may be a
motor generator or a combination of the engine E and the motor generator.

[0062]The vehicle-speed detector 52a may estimate the vehicle speed from
the wheel speeds of the front wheels Wf and the rear wheels Wr.

[0063]While the four-wheel drive vehicle of the embodiment includes the
speed-increasing device 14, the speed-increasing device 14 is not always
necessary and may be omitted.

[0064]While the four-wheel drive vehicle of the embodiment adopts the
automatic transmission T, it can adopt a manual transmission or a
continuously variable transmission (CVT).

[0065]In the embodiment of the present invention, the torque limiter
limits the upper limit of the sub-driving-wheel distribution torque to be
transmitted from the driving source to the right and left sub-driving
wheels via the right and left torque distribution clutches when the
sub-driving wheel distribution torque calculated by the sub-driving-wheel
distribution-torque calculator is higher than or equal to a predetermined
value, both a rotation speed difference of the left torque distribution
clutch and a rotation speed difference of the right torque distribution
clutch are larger than or equal to a predetermined value, and the vehicle
speed detected by the vehicle-speed detector is lower than or equal to a
predetermined value. Hence, it is possible to prevent durability from
being reduced by an excessive actual driving torque produced in the
sub-driving wheels when the main driving wheels slip at the start of the
vehicle. Since there is no need to reduce the output torque of the
driving source at this time, reduction of starting performance of the
vehicle can be minimized.

[0066]In particular, the torque limiter limits the upper limit of the
sub-driving-wheel distribution torque only when both the rotation speed
difference of the left torque distribution clutch and the rotation speed
difference of the right torque distribution clutch are larger than or
equal to the predetermined value. Thus, when one of the right and left
sub-driving wheels on the road surfaces having different coefficients of
friction slips and only the rotation speed difference of one of the right
and left torque distribution clutches becomes larger than or equal to the
predetermined value, driving ability can be ensured while maintaining the
sub-driving-wheel distribution torque.

[0067]Preferably, the torque distribution control apparatus of the
embodiment of the present invention further includes a road-gradient
detector configured to detect a gradient of the road surface. The torque
limiter may limit the upper limit of the sub-driving-wheel distribution
torque when the gradient of the road surface detected by the
road-gradient detector is smaller than or equal to a predetermined value.

[0068]In this case, since the torque limiter limits the upper limit of the
sub-driving-wheel distribution torque when the gradient of the road
surface detected by the road-gradient detector is larger than or equal to
the predetermined value, reduction of climbing ability can be avoided.

[0069]An engine E of an embodiment corresponds to the driving source of
the present invention, an ESC electronic control unit Uc of the
embodiment corresponds to the wheel-speed detector of the invention,
front wheels Wf of the embodiment correspond to the main driving wheels
of the invention, rear wheels Wr of the embodiment correspond to the
sub-driving wheels of the invention, a vehicle-speed detection sensor 52a
of the embodiment corresponds to the vehicle-speed detector of the
invention, an LSD control unit 56 of the embodiment corresponds to the
sub-driving-wheel distribution-torque calculator of the embodiment, a
climbing control unit 58 of the embodiment corresponds to the
road-gradient detector of the invention, and a clutch-torque control unit
60 of the embodiment corresponds to the torque limiter of the invention.

[0070]Obviously, numerous modifications and variations of the present
invention are possible in light of the above teachings. It is therefore
to be understood that within the scope of the appended claims, the
invention may be practiced otherwise than as specifically described
herein.